Winding or lapping machine



0. HAUGWITZ WINDING OR LAPPING MACHINE June 30, 1964 6 Sheets-Sheet 1Filed July 25, 1962 June 30, 1964 0. HAUGWITZ WINDING OR LAPPING MACHINE6 Sheets-Sheet 2 Filed July 25, 1962 June 30, 1964 O. HAUGWITZ WINDINGOR LAPPING MACHINE 6 Sheets-Sheet 5 Filed July 25, 1962 June 30, 1964 o.HAUGWlTZ WINDING 0R LAPPING MACHINE 6 Sheets-Sheet 4 Filed July 25, 1962lllllm IIIIIllyI/l IIIIIIIlIIlIlIIIlll/Il June 30, 1964 o. HAUGWITZWINDING OR LAPPING MACHINE 6 Sheets-Sheet 5 Filed July 25, 1962 June 30,1964 o. HAUGWlTZ WINDING OR LAPPING MACHINE 6 Sheets-Sheet 6 Filed July25, 1962 United States Patent 3,138,913 WINDING 0R LAPPllNG MACHINE OttoHaugwitz, La Celle Saint Cloud, Seine-et-Orse,

France, assignor to Societe Anonyme Geoihoy-Delore,

Paris, France, a French company Filed July 25, 1962, Ser. No. 212,770Claims priority, application France July 27, 1961 8 Claims. (Cl. 57-17)This invention relates to machines for winding tape or strip-likematerial around an elongated core, and is especially though notexclusively concerned with machines for lapping paper, textile plasticor other insulating or conductive materials in helical layers around thecore of an electric cable.

Conventional machines of this kind are frequently designed to subjectthe cable core to a lapping operation directly as the core issues from acable twisting unit. However, the rate of operation of the lappingmachine is limited by the permissible angular velocity that can beimparted to the revolving head of the machine without causing damage tothe revolving parts by centrifugal effects. As a consequence it isfrequently found that the lapping process performed by such machinescannot keep pace with the faster-acting cabling or twisting units. Thusthe full output capacity of these latter units cannot be utilized.

It is an object of this invention to eliminate this limitation andutilize the full output of the cabling units. A related object is toenable the output capacity of lapping machines and the like to bedoubled. This is achieved according to the invention by simultaneouslywinding two helices of tape or strip-like material in diametricallyopposed helices around the cable or other core object to be lapped.

While such dual lapping machines have previously been proposed, none ofthe earlier machines is able to achieve the high degree of precision inrelative positioning of the helical turns that is desirable.

A further object of the invention is to provide a dual lapping machinewhich will be susceptible of a high degree of operating accuracy.

A broader object of the invention is to provide means for winding orlapping strip-like material around a generally cylindrical core, in aplurality of helices of equal pitch circumferentiallydisplaced aroundthe periphery of the core.

A still further object of the invention is to provide a lapping orwinding machine having improved means for rapidly substituting a freshcoil of tape or strip-like material for an exhausted one, therebyreducing machine shut down periods.

Another object of the invention is to provide improved braking meanswhereby the tension of strip or tape-like material will be heldsubstantially uniform throughout a lapping or winding operation despitethe gradual decrease in coil radius due to depletion of the coil.

Yet another object of the invention is to provide means in such amachine for forming a fresh coil of tape or strip-like materialconcurrently with the gradual depletion of a preceding coil during thelapping process, and to form said fresh coil in a position adjacent tothe operative position of the coil from which the material is being fedfor the lapping operation, so that on depletion of the preceding coiland on completion of the fresh coil, the latter can be substituted forthe former by simply sliding it axially into position.

The above and further objects of the invention will become apparent fromthe following description with reference to an exemplary embodimentillustrated in the accompanying drawings, wherein:

FIG. 1 shows an improved lapping machine mostly in axial section;

FIG. 2 is an end view thereof from the cable-input side;

FIG. 3 is an end view from the cable-output side;

FIG. 4 is a partial view on an enlarged scale showing the main andauxiliary coil holders at the output side of the machine;

FIG. 5 is a side view of a two-part coil holder sleeve;

FIG. 6 is an axial sectional view of a variable braking device;

FIG. 7 is a view on lines VIIVII of FIG. 6;

FIG. 8 is an enlarged view from the top of FIG. 6 or 7 showingwear-compensating means;

FIG. 9 is an explanatory force diagram;

FIG. 10 is a side view of the general arrangement of the means forforming a fresh coil simultaneously with the depletion of a precedingcoil; and

FIG. 11 is a view on line XIXI of FIG. 10.

Referring especially to FIG. 1, the lapping machine shown comprises acentral upstanding support 1 carrying at the top thereof a set ofaxially aligned ball bearings 1 through which a hollow shaft 2 rotatablyextends. The shaft 2 is formed centrally with a cylindrical sheavesurface around which a drive belt 3 is trained for rotating the shaft ata suitable angular rate from motor means not shown. A cable 4 to belapped extends freely through the central recess of the hollow shaft 2coaxially therewith, and is adapted to be fed axially therethrough at anessentially constant linear speed, by means not shown.

Mounted for free rotation around the shaft 2 near the opposite ends ofthe shaft are a pair of similar, symmetrically disposed sleeves 5 and 5,each integrally formed with a pair of spaced brake disks or flanges 6,6' at the outer end thereof. Fitted around each sleeve 5, 5 inwardly ofthe brake disks is a removable coil-holder sleeve 7, 7', each carrying acoil of lapping tape 8, 8' thereon. The coil holders 7, 7' are adaptedto be connected for rotation with the related sleeves 5, 5 by means ofdriving pins such as 9, 9'.

The shaft 2 has a pair of transverse flanges 10, 10 extending frompoints near its opposite ends, somewhat beyond the sleeves 5, 5', andcylindrical wall elements 11, 11' are connected to the periphery of eachflange and extend equal axial distances therefrom so as to overlie attheir inwardly directed ends the respective coils 8, 8' and protect thetapes from the damaging effects of air turbulence created by the highangular velocities involved. The flanges 10, 10 and/or walls 11, 11 attheir internal surfaces are further provided with guide means such as12, 12', serving to guide the respective tapes 8, 8 over theirrespective paths of travel as will be presently described. The guidemeans 12, 12 are here shown in the form of roller studs supported,through means not shown, from the surfaces of the drums 11, 11'.However, any other suitable guide means may be used including guidewayor ramp surfaces of suitable configuration over which the tapes 8, 8 maybe arranged to slide. The guide rollers or other means may be madeangularly adjustable. It is noted further that in the various figures ofthe drawing some of the guide rollers have been omitted for clarity.

It will be understood that in operation, as later described in detail,the cable 4 is fed axially at constant speed in the direction shown bythe arrows in FIG. 1, i. e. leftward in that figure. Thus the right endof tubular shaft 2 is the input end, and the left end is the output end.In accordance with the invention, the tapes from both coils 8 and 8'mounted at the outlet and inlet ends of shaft 2 respectively are to beled to a point of the cable 4 positioned somewhat beyond the outlet endof the shaft, being applied to diametrically opposed sides of the cable.More specifically, it will be seen from FIG. 1 that the tape 8 from theroll mounted near the output end is guided by suitably positionedrollers 12 directly to the area 13 of the cable 4 behind the plane ofFIG. 1, whereas the strip 8 from the roll mounted near the input end isfirst guided by rollers 12' provided in drum 11' to a position adjacentthe inlet end of the shaft 2, then ispassed through a longitudinal slot14 formed through the wall of the shaft 2, and constituting a guidewayfrom which said tape 3' emerges at the outlet end, and is then guided byfurther guide rollers 12 supported from drum 11 towards the area 13 soas to be applied onto the surface of cable 4 in front of the plane ofthe drawing, i.e. in an area diametrically opposed to the area ofapplication of tape 8.

It will be understood that with this arrangement, when the shaft 2 isrotated in the clockwise direction as seen from the inlet end, i.e. inthe direction of the arrows shown in FIGS. 2 and 3, both tapes 8 and 8will be wound around the forwardly moving cable 4 to form thereon twocomplementary helices with the turns of each helix filling the gapsremaining between the turns of the other helix. The common pitch of thehelices is determined by the ratio of linear cable feed velocity toangular velocity of rotation.

There is provided means for imparting constant tension to the tapesduring the lapping operations despite decreasing diameter of the coils,and such means operate by applying a variable braking force to thecoilsupporting sleeves 5, by way of brake disks 6, 6. The variablebraking means associated with both coils 8, 8' are substantiallyidentical and will only be described in relation to coil 8 at the outletside of the machine, with particular reference to FIGS. 6, 7 and 8.

A ring member 21 coaxially surrounding the sleeve 5 has a pair ofdiametrically aligned radial extensions or presser members 19,projecting inwardly from it towards the surface of the sleeve betweenthe brake disks 6, and said ring 21 has a pair of aligned pivot rods 22,23 extending outwardly from the ring through apertured bearing lugsprojecting integrally from the surface of flange 10. As shown clearly inFIG. 6, a pair of annular brake disks 15, 16 made of friction liningmaterial are positioned in engagement with the inwardly directedsurfaces of the brake disks 6, and a pair of annular metallic inserts17, 18 are positioned inwardly of the brake disks 15, 16 and engageablewith opposite sides of the presser members 19, 20. Thus, when ring 21 isrotated on its pivots 22, 23, the flat presser members 19, 20 pressoutwardly against the inserts 17, 18 and apply the brake members 15, 16against the inner surfaces of brake disks 6 to apply a braking force tothe coil-holder 5-7. The pivot 22 is provided at its top with a leverarm 33 projecting from it and engageable by a screw 34 serving as anadjustable abutment for the lever. Spring means, not shown, tend torotate the lever arm 33 and with it ring 21 about the axis of pivots22-23 so as to produce the braking action just described. Conveniently,the spring force may be provided by forming pivots 22, 23 as torsionrods fixed at their outer ends.

The ring 21 has a pair of pins 24, 25 projecting normally from the planeof the ring at the root of each of the presser arms 19, 20, and providedat their ends with swivel members 26, 27 seated in recesses 28, 29formed in one of two parallel spaced, rigidly interconnected memberstogether constituting a composite two-armed lever 30 pivoted around thesleeve 5. Projecting from one, the upper, end of the composite lever 30is a roller 31 adapted to be engaged by the tape 8 as it issues from itscoil (also see FIG. 1), ahead of an initial one of the guide rollers 12.At its opposite end the composite lever 30 has a counterweight 32attached to it for dynamic balancing purposes.

The angle or formed between the portion of tape 8 extending from thecoil to the roller 31, and the axis of pivots 22-23 is a maximum whenthe coil is full, and then decreases to a minimum as the coil becomesdepleted. ence the force exerted by the tension of the tape and tendingto rotate the composite lever 30 clockwise (in FIG. 7) increases from aminimum to a maximum value under corresponding conditions. This forcetending to rotate lever 30 is transmitted by way of swivels 27, 28 andpins 24, 25 as a force tending to rotate the ring 21 towards itscentered position in the plane normal to the axis of shaft 2, i.e. ittends to cancel to an increasing degree, as the roll depletes, thetorque applied by torsion rods 22, 23 which tends to force the brakedisks 17, 18 apart and into engagement with the brake drum flanges 6. Itwill readily be understood that by suitably dimensioning the parts ofthe mechanism it is possible in this way to create a resulting forceapplied to the drum 6 that will maintain a constant tension on the tape8 throughout the entire lapping operation, provided the speed ofrotation of the assembly is kept constant. The swivel pins 24, 25 arepreferably threadably adjustable into the ring 21 in order to adjust theforcetransmitting linkage and provide a means of presetting the initialbraking force with regard to the friction coefficient of the linings 17,18 used and other similar factors.

The above braking operation will perhaps be more completely understoodwith reference to the force diagrams shown in FIG. 9. The three diagramsI, II and III relate respectively to the three conditions in which thecoil is full, with a diameter of 240 mm., is partially depleted with adiameter of mm., and is about exhausted with a diameter of 60 mm. Ineach of the diagrams, the respective lever arms 24, 30 and 35 arediagramatically shown with the same relative lengths as in FIG. 1. Theforces involved are indicated as vectors substantially corresponding inlength to the actual magnitude of the forces. The vector P is thepressure force applied by the torque rods, and the vector P is theresultant applied to the brake. It is assumed that the pre-adjustrnentis such that in the condition I, where the roll diameter is maximum, theopposing force component supplied by the tape tension acting on roller31 is zero, so that the braking force is due entirely to the force Pdeveloped by the torsion rods 22-23. In each of the other two positionsII and III the force P is partially offset by a component C due to tapetension. The component C depends on the angle or and on the frictioncoefficient and it is determinable in accordance with the dimensionsspecified above. The force P is a function of tape tension T having therelation P=5.15T in position I and P=1.34T in position III with afriction coeflicient of 0.5 (full line vectors in FIG. 9), and therelation P=6.45T in position I and P=1.70T in position III if thefriction coeflicient is taken as 0.4 (dashed vectors in FIG. 9). It isseen that since each of the ratios 5.15/ 1.34 and 6.45/ 1.70 isapproximately equal to the ratio 240/60 between the tape roll diametersin the corresponding positions, the resulting tape tension T must besubstantially the same in both positions I and III. A similarcomputation would show that the same holds for the intermediatecondition II. It is thus seen that the variable braking arrangementdescribed makes it possible to retain constant tape tension as the rolldiameter decreases throughout the lapping operation.

It is important to ensure that the ring 21 will normally lie in thetransverse plane normal to the axis of shaft 2 in the balanced conditionof the machine in operation. To ensure that this will be the casenotwithstanding, the wear that will normally occur after prolonged use,some type of wear compensation is necessary, and suitable means for thispurpose is shown by way of example in FIG. 8. As shown, the pressermembers 19 and 20 are each made in two parts, 38 and 39, formed withaligned central holes slidably mounted on respective aligned rods 40, 41projecting from opposite sides of the related rod 22 or 23 normally tothe rod and parallel to the axis of shaft 2. The two parts 38 and 39 ofeach presser member 19 or 20 have fiat outer faces engaging therespective metal inserts 17, 18, and have bevelled adjacent surfaces attheir respective ends for variable insertion therebetween of the taperedends of rods 36 the outer ends of which are engaged by the inner ends ofwear compensating screws 37 adjustably screwed into the sides of thering 21. The screws are symmetrically adjusted so as to take upclearance and set the ring 21 in a plane normal to the general axis ofthe machine. It will be noted that during the operation of the machinenone of the parts of the variable braking system described above is inmotion. It is also important to note that with the braking arrange mentdescribed, centrifugal force will not affect the braking action sincethe rotary assembly is dynamically balanced. Similarly, accelerationsand decelerationswhich latter are apt to be very great in machines ofthe character describedwill not affect the braking force nor will theytend to break the tape. Thus, in case of acceleration for instance, thecomposite lever 30 tends to lag behind the remainder of the rotaryassembly due to inertia and will exert opposing forces on the swivels 26and 27 or arms 24 and which forces will cancel one another entirely. Asimilar effect is obtained upon deceleration as inertia causes the lever30 to lead the remainder of the revolving structure.

Means is provided in the lapping machine shown for automaticallybuilding up fresh coils of lapping tape during the lapping operationsand for substituting a fresh coil for an exhausted coil in such a manneras to require the machine to be stopped only a minimum of time, andthereby eliminating the necessity of cutting the cable to be lappedduring the build-up of reserve coils of tape. The above means will nowbe described with reference to FIGS. 1, 4, 5, 10 and ll. It will beunderstood that in connection with this as with other sections of themachine, the description will refer to the arrangement associated withthe outlet coil of tape 8 only, and that a generally identical andsymmetrically disposed arrangement is normally provided in relation tothe inlet coil 8'.

As shown in FIG. 1 and in greater detail in FIG. 4, a supplementarytwo-part tape holder device is provided adjacent the device 5-7,including an inner sleeve 43 freely rotatable around the shaft 2 and anouter sleeve 42 (identical with sleeve 7) removably fitted around theinner sleeve 43 and adapted for being coupled for rotation with sleeve43 by means of a driver pin 45. The inner sleeve 43 is formed with anextension constituting a drive-belt sheave 44 around which a belt 47 istrained, which belt passes at its other end around a pulley 48 (seeFIGS. 10 and 11) which is mounted for free rotation around a drive shaftand is spring-pressed into frictional engagement with another pulley 49keyed on said shaft adjacent pulley 48. Pulley 49 is driven through abelt 50 from an auxiliary electric motor 51, thereby providing afriction drive for the auxiliary coil holder 43-42. One end of a lengthof lapping tape similar to tapes 8 and 8' is adapted to be connectedwith the auxiliary tapeholder sleeve 42 as by engagement into a slot inthe sleeve 42. The said length of tape is supported on a roll 46constituting an external store of tape rotatably mounted on a spindlesupported on the machine frame 1. Conventional tension-regulatingbraking means generally designated 52 are associated with the roll 46for regularizing the rotation thereof.

In operation, the auxiliary motor 51 is energized during alapping-operation in order to rotate the auxiliary coil-holder 42 in asuitable direction through the friction drive 49-48 and belt 47, so thata reserve coil of tape is built up on the auxiliary holder 42 from thestore 46. Preferably automatic means such as a contact 53 (FIG. 10)actuated on the reserve coil on auxiliary holder 42 reaching apredetermined diameter, are provided for cutting off the circuit ofmotor 51. When the coil 8 in operative position has been exhausted, themachine is stopped, preferably also by automatic means as presentlydescribed. The empty coil holder sleeve 7 is then removed from about theinner sleeve 5, for which purpose the sleeve 7 is conveniently made upfrom two interlocking halves as shown in FIG. 5. The substitutecoil-holder sleeve 42, which is similarly constituted, and carrying thereserve 'coil built up as just described, is then slipped into placearound the sleeve 5 in place of the coil-holder 7 by axial displacementleftward according to FIG. 4, while the empty coil-holder sleeve 7 isinserted around the sleeve 43. The free end of the tape of the newlysubstituted full coil on holder 42 now positioned around inner sleeve 5is bonded by any suitable means to the loose end of the lapping tapearound the cable 4, while the loose end extending from the storage roll46 is in turn engaged into a slot provided in the coil-holder sleeve 7,now surrounding inner sleeve 43, in readiness for the build-up of afurther reserve coil. All of the operations just described are easilyand rapidly performed and require only a very short period of machinestoppage. The main motor (not shown) and auxiliary motor 51 are thenrestarted in operation so as to lap a further length of cable whilesimultaneously building up a fresh reserve coil.

It is important that the machine should be stopped, preferablyautomatically, a sufficient time before either of the coils of tape 8,8' has been exhausted in order to avoid the tape running away and avoidhaving to rethread the fresh tape through the slot 14 in shaft 2. Forthis purpose there is shown an actuating finger 54 pivoted to a side ofcoil-holder sleeve 7 (and 42) and adapted to be inserted betweenadjacent turns of the coil during the formation of the reserve coil, soas to overlie a suitable number of innermost turns of tape in the coil,which number is so predetermined as to correspond with the length oftape that is fed out during the period required for the machine to cometo rest after deenergization of its driving motor. As the coil 8 inoperative position approaches its fully depleted condition, the finger54 is released and springs outwardly by centrifugal force, possiblyaided by a spring, thereby acting on a contact 55 provided on a ring 56connected in the motor energizing circuit to deenergize the motor andbring the machine to a stop at the end of said period.

It will be understood that various changes and modifications may be madein the embodiment illustrated and described without exceeding the scopeof the invention. Thus, the machine can readily be modified in order towind more than two tapes around the cable or other cylindrical core tobe lapped. Thus, for example, if it is desired to wind four tapes inequal angularly displaced helices around the core, there may be providedfour coils similar to 8, 8' axially displaced along the length of theshaft each with its associated tape guiding means, including fourlongitudinal slots through the tubular shaft 2 similar to the singleslot 14 shown. A somewhat similar arrangement may be used if desired forexample to provide a multi-layer helical lapping around the cable, e.g.with two layers each similar to the two-helix lapping provided by theembodiment described and shown herein. A further possible modificationlying within the scope of the invention would lie in so predeterminingthe pitch of the helices as to provide overlapping closed helicesinstead of the complementary open helices mentioned earlier herein. Itwill further be noted that some of the teachings of the invention mayfind utility aside from helical lapping machines of the type here shown,as for example in coiling and reeling machines and the like.

What I claim is:

1. A machine for winding laps of tape about a member which is beingaxially advanced through the machine,

said machine comprising: a tubular shaft supported for rotation andthrough which the member is axially advanced, said shaft having an inletend and an outlet end for passage of the member, a pair of coils oflapping tape supported coaxially at either end of said shaft forrotation therewith for thereby rotating around the axially advancingmember, guide means for each of said coils of tape supported on saidshaft for engaging tape from the associated coils and guiding the tapesto the member at angularly spaced locations at a common zone locateddownstream of the outlet end of the shaft, and means for rotating thecoils of tape and respective guide means in synchronization as themember is being axially advanced whereby a plurality of helices of tapeof equal pitch are lapped around the member in angularly displacedrelation, said shaft having an axial slot therethrough extending fromthe inlet end to the outlet end of the shaft, said slot constituting aguideway through which tape from the coil supported on the shaft at theinlet end is drawn by the associated guide means for being wound aroundthe member at said zone.

2. A machine as claimed in claim 1 comprising means rotatably supportingthe shaft substantially centrally between the pair of coils of tapes.

3. The machine as claimed in claim 1, comprising means for applying avariable braking force to each of said coils of tape, and meansresponsive to the diminishing coil radius as the tape is unwound andconnected to said variable braking means for continuously varying thebraking force developed thereby so as to maintain the tension of thetape issuing therefrom substantially constant throughout a lappingoperation.

4. The machine claimed in claim 3, wherein said variable braking meansincludes a pair of axially-spaced brake disks rotatable with each saidcoil; a pair of brake segments positioned between said disks andfrictionally engageable therewith; a presser member inserted betweensaid brake segments and rotatable about a radial axis for forcing saidbrake segments apart into frictional engagement with the brake disks;spring means biasing said presser member in rotation about said axisthereof in one direction; pivoted lever means engageable by said tapefrom each said coil to develop a force that varies continually as theradius of the coil decreases; and means transmitting said variable forceto the presser member for urging the latter in rotation in the oppositedirection.

5. The machine claimed in claim 4, including wear compensating meansadjustable to reposition said presser member in a neutral position aboutsaid axis thereof.

6. A machine for winding a strip of material around a member which isbeing axially advanced through the machine, said machine comprising atubular shaft rotatably surrounding the member, a main coil-holdersurrounding said shaft and detachably connected thereto and adapted tosupport a coil of strip material thereon, means supported on the shaftfor guiding said strip from the coil to the periphery of the member, anauxiliary coilholder surrounding the shaft adjacent the main coil-holderand rotatable relative to the shaft, a store of strip material, meansfor connecting a free end of the strip material from said store to saidauxiliary coil-holder, main drive means for rotating said shaft guidingmeans and said main coil-holder during axial displacement of the memberfor unreeling strip material from said coil and wrapping the same inhelical manner around the member, auxiliary drive means operative forconcurrently rotating said auxiliary coil-holder in a direction forwinding fresh strip material from said store onto said auxiliarycoilholder, and means supporting said auxiliary coil-holder adjacent themain coil-holder for enabling replacement of said main coil-holder uponexhaustion of material therefrom by sliding movement of said auxiliarycoilholder to the position on the shaft assumed by the main coil-holderafter the latter has been removed.

7. The machine claimed in claim 6, wherein said coil holders havecontact-actuator fingers pivoted thereto, said fingers being adapted forinsertion between turns of the coil formed on the auxiliary coil-holderafter a predetermined number of turns has been built up thereon, andcontact means adjacent the main coil-holder in a position to be actuatedby the finger of the main coil-holder on release thereof duringdepletion of the coil thereon, said contact means being connected forarresting said main drive means on actuation thereof by the latter saidfinger.

8. The machine claimed in claim 6, including contact means positionedfor actuation by said auxiliary coil of strip material upon build-upthereof to a predetermined radius, said contact means being operativelyconnected to said auxiliary drive means for arresting the same uponactuation of said contact means.

References Cited in the file of this patent UNITED STATES PATENTS1,565,652 Kochendorfer et a1 Dec. 15, 1925 1,857,820 Rice May 10, 19322,118,136 Bardsley May 24, 1938 2,457,636 Bouget Dec. 28, 1948 2,462,303Bouget Feb. 22, 1949 2,463,211 Spillman Mar. 1, 1949 2,659,192 RipleyNov. 17, 1953 2,782,138 Olson et al. Feb. 19, 1957 2,826,035 Cogger Mar.11, 1958 2,921,427 Stark et a1. Jan. 19, 1960 FOREIGN PATENTS 577,646Germany June 2, 1933

1. A MACHINE FOR WINDING LAPS OF TAPE ABOUT A MEMBER WHICH IS BEINGAXIALLY ADVANCED THROUGH THE MACHINE, SAID MACHINE COMPRISING: A TUBULARSHAFT SUPPORTED FOR ROTATION AND THROUGH WHICH THE MEMBER IS AXIALLYADVANCED, SAID SHAFT HAVING AN INLET END AND AN OUTLET END FOR PASSAGEOF THE MEMBER, A PAIR OF COILS OF LAPPING TAPE SUPPORTED COAXIALLY ATEITHER END OF SAID SHAFT FOR ROTATION THEREWITH FOR THEREBY ROTATINGAROUND THE AXIALLY ADVANCING MEMBER, GUIDE MEANS FOR EACH OF SAID COILSOF TAPE SUPPORTED ON SAID SHAFT FOR ENGAGING TAPE FROM THE ASSOCIATEDCOILS AND GUIDING THE TAPES TO THE MEMBER AT ANGULARLY SPACED LOCATIONSAT A COMMON ZONE LOCATED DOWNSTREAM OF THE OUTLET END OF THE SHAFT, ANDMEANS FOR ROTATING THE COILS OF TAPE AND RESPECTIVE GUIDE MEANS INSYNCHRONIZATION AS THE MEMBER IS BEING AXIALLY ADVANCED WHEREBY APLURALITY OF HELICES OF TAPE OF EQUAL PITCH ARE LAPPED AROUND THE MEMBERIN ANGULARLY DISPLACED RELATION, SAID SHAFT HAVING AN AXIAL SLOTTHERETHROUGH EXTENDING FROM THE INLET END TO THE OUTLET END OF THESHAFT, SAID SLOT CONSTITUTING A GUIDEWAY THROUGH WHICH TAPE FROM THECOIL SUPPORTED ON THE SHAFT AT THE INLET END IS DRAWN BY THE ASSOCIATEDGUIDE MEANS FOR BEING WOUND AROUND THE MEMBER AT SAID ZONE.